Infinitely variable speed transmission



May 29, 1956 A. G. BADE 2,747,434

INFINITELY VARIABLE SPEED TRANSMISSION 2 Sheets-Sheet 1 Filed May 14,1951 Imventor 1Q. F250 6-. @405 B (Ittomeg y 9, 1956 A. G. BADE2,747,434

INFINITELY VARIABLE SPEED TRANSMISSION 7 Filed May 14, 1951 2Sheets-Sheet 2 Imventor flAFEE'D 6-. E1405 Gttorneg United States PatentINFINITELY VARIABLE SEEED TRANSNIISSION Alfred G. Bade, Milwaukee, Wis.,assignor to The Falk Corporation, Milwaukee, Wis., a corporation ofWiscousin Application May 14, 1951, Serial No. 226,163

29 Claims. (Cl. 74-796) This invention relates to improvements ininfinitely variable speed-changing power transmissions of the type inwhich the speed of one shaft varies while the speed of the other shaftis constant, the speed of the one shaft varying from above to below thatof the constant speed shaft.

Where prime movers are used chiefly to supply power for a given purposefor which the power demand varies widely, it may also be desirable touse the same prime mover as a source of power for a second devicerequiring a constant speed. An example of a drive meeting the aboveconditions, is an engine of aircraft where the speed of the accessorydrive shaft (which may be connected by gearing with the engine crankshaft), may vary from 3000 to 10,000 R. P. M. and where it is desired todrive an alternating current generator at a constant speed of 6000 R. P.M. during the time the engine speed varies, for example, between 1000and 3300 R. P. M. The mechanical devices heretofore available, by whichan infinite speed variation could be obtained over a sufficiently widerange, have a number of limitations such as the amount of powertransmissible, the gyroscopic effect of some parts which producesextremely high localized pressures, and unbalanced forces which tend tocause variation in the operation and short life of the speed changingdevices.

It is therefore an object of the present invention to provide aninfinitely variable speed changing transmission in which the speed ofthe one shaft varies from below to above the speed of another shaft tobe driven at a constant speed value.

Another object of the invention is to provide a variable speed changingtransmission in which power is transmitted at an infinitely variablerate from a shaft operating at a speed less than, or several times morethan, the speed of another shaft which is to be operated at a constantspeed.

Another object of the invention is to provide an infinitely variablespeed changing transmission in which a major portion of the powertransmitting elements float or shift their position relative to otherparts to equalize the contact pressures between the parts.

Another object of the invention is to provide an infinitely variablespeed-changing transmission of the type in which the speed is varied byinteraction of mechanical elements and in which the speed changingelements are interconnected to divide the torque reaction and totransfer such reaction to relatively stationary parts.

Another object of the invention is to provide an infinitely variablespeed-changing power transmission of the type in which the speedchanging elements are sets of friction or adhesion elements and in whichsuch elements are subjected substantially only to centrifugal force toexert the necessary traction effort, a constant speed being obtained byvarying the permitted circumference upon which the friction elements maycentrifugally seek their path of travel against their complementaryfriction element.

Another object of the invention is to provide an infinitely variablespeed-changing power transmission in 2,747,434 Patented May 29, 1956"ice which rollers and disks are the speed-changing adhesion typeelements and have coacting surfaces at the same angle so that a powerfulwedging action may be exerted on one set of the elements with littleforce applied to the other set of elements to shift the position of thesaid one set of elements relative to the axis of the variable speedshaft driving the said one set of elements.

A further object of the invention is to provide an infinitely variablespeed-changing power transmission utilizing rollers and disks as thespeed changing elements and in which the rollers are independent and actindependently upon the disks for changing the speed of one of the shaftsof the transmission.

And another object of the invention is to provide an infinitely variablespeed-changing transmission in which the speed changing elements are ofthe adhesion or friction type and are in themselves symmetrical andsymmetrically arranged so that gyratory forces and vibrations areminimized, in which the bearings are not required to withstand pressuresvarying within wide limits. The forces involved are largely centrifugaland in an adjustment for change of ratio these forces are kept inbalance. The speed changing elements while mounted for centrifugalresponse for movement to a different circumferential path, are confinedby strong, balanced rings which not only provide control surfaces tochange speed ratios, but also provide the working surfaces against whichthe adhesion or friction elements operate.

Generally, the present embodiment of the invention comprises a shaft tobe driven at constant speed from a shaft driven at variable speedsranging from below the constant speed value to several times such value.The variable speed shaft bears a number of rollers on spokelikeprojections from the shaft so that centrifugal force acts on the rollersupon rotation of the shaft. The rollers are movable radially of theshaft and rotate on their axes due to friction between the rollers andmovable disks in contact with the rollers at diametrically oppositepoints. The contacting surfaces of the rollers are at an angle to theaxis of the rollers and the contacting disk surfaces are at a similarangle. The position of the disks relative to the rollers controls thedistance of the rollers from the axis of the variable speed shaft andhence varies the mechanical advantage obtained by enlarging ordiminishing the radius of the path traveled by the rollers. Thecentrifugal force may thus be altered to counteract or compensate forthe different speeds of rotation of the variable speed shaft.

The disks are mounted for movement at an angle to the axes of therollers as well as toward and away from such axes; wherefore, the disksadjust themselves or float as required by the pressures acting thereon.A yoke acts on oppositely threaded parts for causing movement of thedisks toward and away from each other as the yoke is moved. The forcerequired for moving the yoke is small and while the instant inventioninvolves no specific control of the yoke, it will be understood that anyform of manual or automatic means for adjusting the yoke may beutilized.

The roller contacting surfaces of the disks are conical planes and theroller edges contacting with such surfaces are crowned to obtainsubstantially a line effect of such surfaces. The pressures actingbetween the rollers and disks are a pressure which is normal orperpendicular to the plane of the disks at the line of contact, and atangential pressure in the plane of rotation of the line of contact. Thepressures between the rollers and each of the disks are equalized bytransmitting reaction from a fixed disk by way of gearing to the otherand rotating disk. Power is transmitted from the driving shaft to 7 3the driven shaft by way of the rollers and planetary gearing connectingthe rollers with the driven shaft.

Objects and advantages other than those above set forth, will beapparent from the following description when read in connection with theaccompanying drawing, in which:

Fig. 1 is a'view partially in elevation and partially in section on aplane transverse to the direction of power flow through a transmissionembodying the present invention.

" Fig. 2 is a partial elevation and partial sectional view taken on theplane of line 22 of Fig. 1; and

' Fig. 3 is an enlarged somewhat diagrammatic view illustrating the pathof power'fiow through the device. Referring to the drawings by referencenumerals in which like numerals designate. like parts, a housing isformed from a member having a side Wall portion 'and% an end wallportion 11 integral therewith, the end wall having a central apertureand a flange 12 defining the aperture and reentrant into the side wallhousing portion. Another end wall portion 13 is formed as a sub-'stantially annular disk attachable to the side wall 10, the two endwalls and the side wall providing an enclosure with aligned aperturesthrough the end walls. The housing end wall 13 receives and has attachedthereto a 7 plate 14with a cylindrical portion internally splined asindicated at 15. Plate 14 provides a mounting for a bearing 16 and hasattached thereto a lubricant seal 17 in which a first shaft 18 ismounted. In the present instance such shaft is assumed to be a powerinput shaft and to be driven at speeds varying from 3000 to 10,000 R. P.M.

The shaft 18 has an enlarged portion within the housing to provide aplurality of sockets (six in number in the present construction) whichare equidistant about the shaft periphery and have their center lines onradii of .the shaft.- Spoke-like members are severally mounted in theshaft sockets to provide axles for the rotation of elements mountedthereon. A bushing type bearing 26 is mounted on each of the axles 25and seats on the enlargement of shaft 18 to support a planet bevelpinion 27 with a hub-like extension 28 from one side of the gear. Thegear hub extensions 28 are severally supported on bearings 29 mounted onthe axles 25 and each of the gear hubs 28 supports a bearing on'which ismounted a freely rotatable bevel pinion 30. The external surfaces of thegear hubs 28 are splined for severally receiving the internal splines ofrollers 33 having aperipheral adhesion .or'friction surface at an angleto the axis of the rollers andcrowned for coaction with other elementsto be described. The contact diameter of each roller 33 is equal to thepitch diameters of bevel pinions and 27. The members 25 are joined attheir outerends by a ring 35 and provide axles for rotation of thepinions 27 and their hub extensions 28. The hub extensions form quillshafts for the rollers, on which the rollers may move toward or awayfrom the axis of the variable speed shaft 18 and on radii of said shaft.

A hollow and second shaft (assumed herein to be the output shaft to bedriven at a constant speed of 3,300 R. P. M.) extends into the housingthrough the aperture in the housing end wall 11 and is internallysplined as indicated at 41 for receiving the shaft of a device to bedriven at constant speed.

The second shaftprovides a support in part for first shaft 18 by way ofbearing 42 for the stub end of first shaft 18. Second shaft 41 ispreferably part of a sleevelike extension 44 forming the hub of a bevelgear 45. Bearings 46 support the'shaft 44 and bevel gear 45 in theflange 12 of the housing end wall 11 and the space between such flangeand the gear hub is closed by a seal 47. An oil seal 48 is interposedbetween the ends of second shaft splines 41 and bearings 42. It will beseen that the bevel'pinions 27 engage the bevel gear 45,

A bevel gear 53 is fixed on the end of the housing which are mounted forfree rotation on the gear hubs 28 and the gear 53 is externally splinedfor a purpose which will appear hereinafter. The fixed gear ring 53extends about the axes of shafts l8 and 41 and engages the idler bevelpinions 30 on one side of a plane through the axes of the spoke-axles25. A second bevel gear 55, generally similar to the gear 53 has asplined portion similar to that of the gear 53 and is mounted onbearings 56 on the sha'ft'18. The second gear 55 also extends about theaxes of the shafts 1S and 41 and engages the idler bevel pinions 30 onthe other side of a plane through the axes of spoke-axles 25.

The splines of the gears 53 and 5 5 are severally engaged by splines onthe hub-like portions of substantially conical disks 53 and 59, the disksplines being internally of the hubs thereof. The disks 58 and 59 arealso on opposite sides of a plane through the axes of the spokeaxles 25and define a space of which two sides are at an angle similar to theangle of the adhesion surfaces on the rollers 33. Hence, a line on eachof the crowned, adhesion surfaces of the rollers may contact with theadjacent and plane surfaces of the disks at the ends of a diameterthrough the rollers. By movement of the disks, pressure may be exertedon the rollers to cause positioning of such rollers at any desireddistance from the axis of the shaft 18.

The splines on the disks 58, 59 are also everally engaged by angle ringshaving splined or toothed peripheral edges acting as dental connectionswith the disks. One ring 64 is supported on a bearing 65 shown as beingof the needle type and the ring has a cylindrical portion with anexternal thread thereon. Another angle ring 62 has a portion supportedon a bearing 63 within another ring 66 flanged for defining asubstantially cylindrical space, the ring 66 having splines 67engageable with the splines 15 of housing plate 14 and having anexternally threaded cylindrical portion similar to the threaded portionof ring 64, the two threads mentioned being of the same coupling withthe gear 55. The bearing 65, however,

supportsthe disk 53 in radial direction so that such disk can adjustitself only in the direction of the axis of shaft 18. The entiresub-assembly comprising disks 58 and 59 and the members supporting disk59 are thus selfcentering.

The cylindrical portions ofring 64 and member 66 extend along the axesof the shafts 18 and 44 and everally receive threads formed on the legs70, 71 of a hollow ellipsoidal yoke having a thread 72 at leastpartially about the periphery of the yoke to serve as a worm wheelfragment. The worm wheel 72 is engaged by a worm 73 mounted in bearings74 and 75 in a portion of the housing side wall. The dental connectionsof the disks 58, 59 and angle rings 62, 64 are limited by pairs of ring76, 77, snapped into grooves in the disk dentals.

The housing is fixed to the prime mover and the gear 53 is fixed to thehousing and holds the disk 58 against rotatable movement relative tothehousing. The gear 55 is however rotatable on the bearings 56 so thatsuch ring gear does not restrain movement of the disk 59, Angle ring 62is generally annular and is mounted upon its bearing 63 for rotationwith disk 59, while angle ring 64 is likewise annular and isdentallyconnected with disk 58, and since disk 58 is dentally connectedwith gear 53 fixedly mounted with respect to flange .12 and the housing1011, the angle ring 64 does not rotate independently of the housing.However, each of the angle rings '62 and 64 is adjustable parallel withthe axes' of shafts 18, 41, 44 under control of the yoke. The

relatively high normal pressures between the adhesion elements areconfined to the yoke sub-assembly and do not react on or revert to otherparts where such pressures would be disturbing to the usual operatingconditions of the device. When the yoke 70, 71 is rotated, the anglering 64 and the flanged ring 62 are urged toward or away from eachother. Hence, the disks 59 and 58 are moved toward or away from eachother to vary the space between the disks. Change of disk spacing allowsthe rollers to move from the positions shown, outwardly under the actionof centrifugal force, or forces the roller inwardly from an outwardposition as the disks 59 and 58 are pressed toward each other. Theself-aligning dental connection between rings 67 and 62 permits the disk59 to adjust itself at an angle to a plane through the axes of the axlemembers 25 so that the pressures at all of the roller-disk contactpoints are always equal and provide a large number (twelve) contactpressure points by which power may be transmitted. The torque reactionson disks 58 and 59 are equalized by the action of the idler bevel gears30 meshing with the ring gears 53 and 55,

Referring now to Fig. 3, assuming that the shaft 18 is rotated in thedirection shown and that the spokeaxles 25 and planet bevel gears 27 androllers 33 are rotating about the axis of the shaft, the rollers 33rotate about their axes due to friction between the rollers and thedisks. Roller rotation is transmitted to bevel pinions 27 which meshwith bevel gear 45 and the motion of such gear is transmitted to outputshaft 41.

When the input speed is at its highest value, the rollers 33 should bein the position A shown (in Fig. 3), and should move from that positiontoward the dotted line position B as the input shaft speed decreases.Such movement is accomplished by turning the yoke 70, 71 in a directionto move disks 58 and 59 away from each other to reduce a restrainingaction of the disks on the rollers and allow the rollers to assumeposition B. As the rollers 33 move radially outwardly from the positionA to position B duringthe continued rotation of shaft 18, it will beobvious from the above description that the path of travel of theperipheral frictional surface against the surfaces of the disks 58, 59will be increased, and even though the speed of rotation of the shaft 18may be reduced, and speed of rotation of the rollers 33 about their ownaxes will be increased. The increased speed of rotation of the rollersis reflected of course in increased speed of rotation of the beveledpinions 27 on the respective splined hubs on which the respectiverollers are mounted. Since the speed of rotation of the driven shaft 41is a composite of the speed of rotation of the input shaft 18 and thespeed of rotation of the beveled pinions 27 engaged with beveled gear45, it is apparent that the increased speed of the rollers 33 as theyare adjusted outwardly upon the disks 58, 59 determines the speed ofrotation of shaft 41. Furthermore, it will be noted that as the speed ofrotation of shaft 18 is reduced, and desirably the shaft 41 should beincreased in speed of rotation with reference to the given speed of theshaft 18 so as to hold the constant speed of shaft 41, rollers 33 willbe moved outwardly upon the splined hubs of the beveled pinions 27 intopositions where they will respond to increased centrifugal force.Increased centrifugal force upon the rollers 33 results in a much moreintimate contact and a much more effective frictional engagement betweenthe outer surfaces of the rollers 33 and the disk surfaces against whichthey impinge. In addition to these factors, there is the added factorthat while called upon to perform a given work while shaft 18 is at aslower speed, the friction elements or rollers 33 are permitted totravel a much increased length of circumferential path. Viewing thisfrom the point of view of friction drive, this is equivalent to anincrease in moment arm. In the contrary condition where the speed ofshaft 18 increases, the maintenance of constant speed on the outputshaft requires the adjustment of the disks 58, 59 toward one another soas to confine the rollers 33 in positions more closely approaching theaxes of shafts 18, 44. Frictional contact pressures between the rollersand the disks remain high because the centrifugal forces are high at thehigher shaft speed and the speed of rotation of the beveled pinions 27is relatively reduced because of shorter path of travel defined by thepath of contact between the roller 33 and a particular disk.

When input speed rises from a low value in which the rollers are inposition B, the yoke is turned to bring disks 58 and 59 toward eachother. A powerful wedging action is thus exerted on the rollers to movethem toward the axis of shaft 18 and thus reduce the moment arm of thecentrifugal force.

To explain the operation of the transmission above described, it may besaid that the input or driving shaft 18 is connected to the output ordriven shaft 41 by power connections therebetween including the beveledpinions 27 mounted upon their respective radial shafts and beveled gear45 on the driven shaft 41. In the absence of other drives, there wouldof course be no power transmitted between shafts 18 and 41 because thebeveled pinion 27 would act merely as an idler, but if some constrainingmeans to influence the speed of rotation of the beveled pinion 27 isprovided, then power may be transmitted from the one shaft to the other,and it is with the constraining means influencing the speed of rotationof this driving connection that this invention is concerned.

It has already been explained that the pitch diameter of the roller 33is the same as the pitch diameter of the beveled pinion 27, and sincethe roller is splined upon the hub of the beveled pinion, the two rotatetogether at the same speed. Assuming that the roller 33 is in theposition indicated by the dot-dash line A in Fig. 3, and the disks 58,59 are so adjusted as to confine the roller in this position againstoutward radial centrifugally induced sliding motion on the splines ofthe beveled pinion hub, the rotation of the driving shaft 18 will causethe roller to be driven frictionally by the fixed disk 58 at a number ofrevolutions per minute dictated by such fn'c tional engagement anddetermined by the lineal extent of the circumference of the particularcircle which the roller follows in its path around the disk in view ofthe particular number of R. P. M. of the shaft 18. Obviously, since thispath of travel is along a circumference of a circle which is greater inradius than the circumference which is followed by the beveled pinion27, and the beveled pinion 27 is in engagement with beveled gear 45, thebeveled pinion tends to rotate under the constraint of the roller 33faster than it would normally rotate if no constraint were put upon itand it were to rotate as an idler in mesh with the gear 45. Therefore,the more rapidly rotated pinion 27 forces shaft 41 to rotate in thedirection opposite the direction of rotation of shaft 18 as shown by thearrows in Fig. 3.

Despite centrifugal force upon the roller 33 tending to throw itoutwardly upon the splines of the hub of pinion 27 even though therotation of shaft 18 may be rapid, disks 5%, 59 are held by the yoke 70,71 and the roller is confined so that a wedging action takes place withresultant adhesion force to increase the efficiency of the engagementfor power drive.

When the disks 58, 59 are adjusted outwardly to permit an outwardadjustment of the roller 33 on its spline mounting, the roller willassume a position to take an increased circumference upon an increasedradius relative to shaft 18. This will give greater speed of rotation tothe pinion 27 and greater speed of rotation of shaft 41 in the directionof the arrow. Throughout the range of adjustment of the disks 5%, 59,the disks move equally oppositely under the threaded adjustment of theyoke upon the angle rings 62 and 64, and when they move toward eachother to force the roller 33 inwardly radially to follow a shorter andcircumferentially smaller path, the

centrifugal forces upon the plurality of rollers 33 are balanced sincerollers are forced to conform to the same circumferential path and allof the major centrifugal forces are absorbed by the rigid disks 58, 59or by the shafts 25, or by the yoke '70, '71. Any of these major forcescan only be carried by the bearings in an incidental way.

It will be understood that a selected gear ratio between pinion 27 andgear 45 may be such that at a particular speed desired for a heavy powerrequirement the roller 33 may be positioned outwardly radially to anextreme position of adjustment and in such outward position ofadjustment greater centrifugal forces are applied to insure a morepositive frictional engagement between roller 33 and disks 58, 59.

While the disks 58, 59 hold the rollers 33 in balanced restraint againstcentrifugal force, the rollers 33 and the 7 idler pinions 35) drive thegears 55 and the parts dentally connected with such gears 55, but suchdrive is converted into rotary motion of the disk 59, the gear 55, theangle ring 62 and ring 66. The disk-yoke sub-combination includesflexible connection means whereby the disks adjust axially and as a unitto equalize the pressures of the rollers on both disks.

As compared to prior adhesion or mechanical types of speed changingdevices, the present structure provides the advantages of minimumgyroscopic forces, of obtaining torque at the ends of a diameter of eachplanetary adhesion element and of providing a plurality of independentadhesion planetary elements with equalized pressures at all pairs ofadhesion surfaces. The gyroscopic forces are those forces acting on allparts mounted on the spokes 25 and which rotate both about the axis ofthe shafts 18, 41-44- and about the spokes 25 of which the axis isperpendicular to the shaft axis. The present structure thereforeprovides capacity for transmission of greater quantity of power than waspossible with the prior devices as well as producing increased life andquieter operation even at such greater capacity. For a given capacity,the present device is more compact than those now known and the adhesionelements are symmetrical so that the vibration is minimized. Thereaction or reversion of pressures other than the usual operatingpressures on the bearings, is minimized so that less heat is produced,the bearings sizes may be decreased and adequate lubrication is simplerthan in other adhesion types of speed exchangers.

Although but one embodiment of the present invention has beenillustrated and described, it will be apparent that various changes andmodifications may be made therein without departing from the inventionas defined in the appended claims.

I claim:

1. In a power transmission for changing a variable speed to a constantspeed and vice versa, a variable speed shaft, rollers subjected tocentrifugal force by rotation of the variable speed shaft, the rollersseverally having a peripheral edge at an angle to the axis of therollers, a constant speed shaft, gearing connecting the rollers and theconstant speed shaft, 2. pair of disks each having a surface engageablewith the rollers at diametrically opposite points on the rollers andsaid surfaces being radially outwardly convergent, the disks having theadjacent and roller contacting surfaces at the angle of the peripheraledges of the rollers, and means for mounting the disks for movement in agiven relation with the roller axes and at an angle to such axes.

2. In a power transmission for changing a variable speed to a constantspeed and vice versa, a housing, a variable speed shaft, rollers mountedon and adjustably slidably subject to centrifugal force by rotation ofthe variable speed shaft, a constant speed shaft, gearing connecting therollers and the constant speed shaft, a pair of movable disksfrictionally engaging the rollers therebetween and providing a radiallyoutwardly con- 8 stricted annular path for the rollers, the disksseverally having internally splined hub extensions, and peripherallytoothed rings engaging the disk splines for movement of the disks"laterally relative the axis of the rollers, one of the toothed ringsbeing rotatably mounted on portions of the housing.

3. In a power transmission for changing a variable speed to a constantspeed and vice versa, a variable speed shaft, rollers subjected tocentrifugal force by rotation of the variable speed shaft, a constantspeed shaft, gearing connecting the rollers with the constant speedshaft, a pair of disks for severally and frictionally engaging all ofthe rollers, means for mounting the disks for movement of the adjacentfacesthereof relative to' the roller axis and for equalizing rollerpressures on the disks, and means for moving the disks toward and awayfrom the rollers while maintaining the given relation with the rolleraxis one of the disks being rotatively relativeiy fixed and the other ofsaid disks being mounted for relatively free rotation.

4. In a power transmission for changing a variable speed to a constantspeed and vice versa, a housing, a variable speed shaft, rollerssubjected to centrifugal force by rotation of the variable speed shaft,a constant speed shaft, gearing connecting the rollers to the constantspeed shaft, a pair of disks severally engageable with each of therollers, means for mounting the disks for movement in a given relationwith the plane of the roller axes and at an angle to such plane, andmeans movably engaging the housing for moving the disks toward and awayfrom each other, said disks being shaped to provide an outwardlyconvergent annular path for the rollers.

5. In a power transmission for changing a variable speed to a constantspeed and vice versa, a housing, a

variable speed shaft, rollers subjected to centrifugal force by rotationof the variable speed shaft, a constant speed shaft, gearing connectingthe rollers to the constant speed shaft, means mounting the disks formovement in a given angular relation with the plane including theseveral axes of the rollers and at an angle to such plane, a yokethreadedly and severally engaging with the disks, and means movablymounted in the housing for rotating the yoke and thereby moving thedisks toward and away from the plane of the roller axes.

6. In a power transmission for changing a variable speed to a constantspeed and vice versa, a variable speed shaft, rollers subjected tocentrifugal force by rotation of the variable speed shaft, a constantspeed shaft, gearing connecting the rollers to the constant speed shaft,a pair of opposed disks for movement in a fixed angular relationshipwith the roller axes, means for moving the disks equally and oppositelytoward and away from the rollers, and means for equalizing the pressurebetween the several contacting surfaces of the rollers and the disks.

7. In a power transmission for changing a variable speed to a constantspeed and vice versa, a housing, a variable speed shaft, a cageextending radially from the shaft, rollers mounted on and movable in thecage radially of the shaft for subjecting the rollers to a variablecentrifugal force upon rotation of the variable speed shaft, the rollershaving a friction surface at an angle to the roller axes, a constantspeed shaft, gearing connecting the rollers with the constant speedshaft, movable disks frictionally engaging the rollers, the disks havingadjacent surfaces at the'angle of the roller friction surfaces andseverally having splines, toothed rings movably mounted on the housingfor severally engaging the disk splines, a member movably in the housingfor acting on the rings and thereby moving the disks toward and awayfrom each other, means movably mounted on the housing and engaging thering-actuating member for adjusting the rings and thereby moving thedisks toward and away from the rollers, and gearing connecting the disksfor equalizing the pressure between the rollers and the disks and fortransmitting torque reactions therebetween.

8. In a power transmission for changing a variable speed to a constantspeed and vice versa, a stationary housing, a first shaft rotatablymounted in the, housing, rollers driven by and movable on radii of thefirst shaft, disks movable toward and away from each other forfrictional contact peripherally with the several rollers atdiametrically opposite points thereof, one disk being rotatable and onedisk being non-rotatable relative to the housing, means for moving thedisks and thereby varying the positions of the rollers radially of thefirst shaft, gearing connected with the rotatable disk and driventhereby, the gearing being engageable with the housing for transmittingreaction torques from the disks to the housing, and a second shaftconnnected with the rollers for rotation thereby at speeds dependentupon the positions of the rollers radially of the first shaft.

9. In a power transmission for changing a variable speed to a constantspeed and vice versa, a stationary housing, a first shaft rotatablymounted in the housing, rollers mounted and movable on shafts positionedon radii of the first shaft, disks radially outwardly convergent andmovable toward and away from each other for frictional contactperipherally with the several rollers at diametrically opposite pointsthereof, one disk being rotatable and one disk being non-rotatablerelative to the housing, means for moving the disks and thereby varyingthe positions of the rollers radially of the first shaft, a gearconnected with and driven by the rotatable disk, a gear mounted on thehousing, an idler gear connecting the said gears for transmittingreaction torque on the non-rotatable disk through the gears to thehousing, speed to a constant speed and vice versa, a stationary and asecond shaft connected to the rollers for rotation thereby at a speeddependent on the position of the rollers radially of the shaft.

10. In a power transmission for changing a variable housing, a firstshaft rotatably mounted in the housing, rollers mounted and movable onshafts disposed on radii of the first shaft, disks having radiallyoutwardly convergent surfaces and movable toward and away from eachother for frictional contact peripherally with the several rollers atdiametrically opposite points thereof, one disk being rotatable and onedisk being non-rotatable relative to the housing, means for moving thedisks and thereby varying the positions of the rollers radially of thefirst shaft, a gear mounted on the first shaft for rotation relativethereto and driven by the rotatable disk, a gear fixed on the housing,idler gears severally associated with the rollers and connecting thesaid gears for transmitting reaction torque between the disks andthrough the gears to the housing, and a second shaft connected with therollers for rotation thereby at a speed dependent on the position of therollers radially of the first shaft.

11. In a device of the character described, a relatively stationaryhousing having centrally aligned shafts therethrough and an infiniteratio transmission mounted in the housing for power drive from one shaftto the other, the housing having a cylindrical flange encompassing oneof the shafts to provide internally of the housing a mount for a portionof the transmission, an annular mount slidably receivable upon one ofthe shafts in spaced relation to the cylindrical flange and engageablewith the housing to prevent rotation on the shaft, an annular threadedtransmission adjusting collar slidable on the cylindrical flange and athreaded surface on the annular mount, a hollow ellipsoidal yoke havingmargins threaded to engage the threaded collar and threaded annularmount, the parts being threaded to move the collar and mount equally andoppositely upon rotation of the yoke, and transmission apparatus withinthe hollow yoke for power transmission from one shaft to the other, saidapparatus including spoke-like shafts extended radially from one of theshafts and provided with centrifugally responsive rollers connected topinions forming part of a gear connection with a gear on the othershaft, a friction surfaced disk mounted to the collar for movementtherewith whereby to move the friction surface against the rollers, saidfriction surface being at an angle to the spoke shafts for outwardradially convergence theretoward whereby to adjustably restrict theradius of the circumferential path to be travelled by the rollers and tochangethe ratio of the power drive from shaft to shaft.

12. The device of claim 11 wherein two friction disks face one anotherand one is mounted to the threaded collar and the other is mounted tothe annular mount, one of said disks having bearing surfaces for freerotation with respect to the member on which it is mounted, the two disksurfaces being outwardly radially convergent.

13. The device of claim 11 in which the housing and the yoke areadjustably interconnected for threaded adjustment of the margins of theyoke in relation to the mounts and each of the mounts has a disk mountedthereto for equal movement to and from the other in response to suchadjustment.

14. In a power transmission, a drive shaft, a driven shaft coaxial withthe drive shaft, the disks being axially spaced and having opposed facesconverging outwardly from the shafts, rollers urged outwardly uponrotation of the drive shaft into pressure contact and in rollingengagement with the opposed faces of the disks, gearing connecting therollers with the driven shaft for rotation thereof, and means foradjusting the spacing of the disks for thereby controlling positioningof the rollers radially of the disks and varying the speed of rotationof the driven shaft.

15. In a power transmission, a drive shaft, a driven shaft coaxial withthe drive shaft, a pair of disks coaxial with the shafts, the disksbeing axially spaced and having opposed faces converging outwardly fromthe shafts, rollers urged outwardly upon rotation of the drive shaftinto pressure contact and rolling engagement with the opposed faces ofthe disks, gearing connection the rollers with the driven shaft forrotation thereof, at least one of the disks being rockably mounted forequalizing pressure of the individual rollers on the disks, and meansfor adjusting the spacing of the disks for thereby controllingpositioning of the rollers radially of the disks and varying the speedof rotation of the driven shaft.

16. In a variable speed transmission, the combination of coaxial drivingand driven shafts, a pair of opposed disks disposed coaxially of andspaced axially of the shafts, a set of planet rollers in rollingengagement with and between the disks, one of the disks being rockablymounted to effect pressure contact thereof with the individual rollersof the set of planet rollers, means for mounting the rollers formovement radially of the disks to vary the relative motion between therollers and the disks, gearing connecting the rollers with the driveshaft for rotation thereof, and means for achieving the spacing of thedisks for thereby controlling the positioning of the rollers radially ofthe disks and for varying the speed of rotation of the driven shaft.

17. In a power transmission, a drive shaft, a driven shaft coaxial withthe drive shaft, a pair of disks coaxial with the shafts, the disksbeing axially spaced and having opposed faces converging outwardly fromthe shafts, rollers movable into pressure contact and rolling engagementwith the opposed faces of the disks, means for mounting the rollers onthe drive shaft for rotation thereby and movement radially thereof,gearing connecting the rollers with the drive shaft for rotation of therollers and connected with one of the disks for rotation thereof andmeans for adjustably spacing the disks for thereby controllingpositioning of the rollers radially of the disks and varying the speedof rotation of the driven shaft.

18. In a power transmission, a drive shaft, a driven shaft coaxial withthe drive shaft, a pair of disks coaxial with the shafts, the disksbeing axially spaced and having opposed faces Converging outwardly fromthe shafts, rollers movable upon rotation of thedrive shaft intopressure contact and rolling engagement with the opposed faces of thedisks, gearing connecting the rollers with the driven shaft for rotationthereof, means for rendering the gearing responsive to relative motionbetween the disks and the rollers, and means for adjusting the spacingof the disks for thereby controlling positioning of. the rollersradially of the disks and varying the speed of rotation of the drivenshaft.

19. In a power transmission, a drive shaft, a driven shaft coaxial withthe drive shaft, a pair of disks coaxial with the shafts, the disksbeing axially spaced and having opposed faces converging outwardly fromthe shafts, rollers mounted on and movable upon rotation of the driveshaft into pressure contact and rolling engagement with the opposedfaces of the disks, gearing connecting the rollers with the driven shaftfor rotation thereof, and rotary means coaxial with the shafts formoving the disks equally and oppositely toward and away from each other.

20. In a power transmission, a drive shaft, a driven shaft coaxial withthe drive shaft, a pair of disks coaxial with the shafts, the disksbeing axially spaced and having opposed faces converging outwardly fromthe shafts, one of the disks being rotatable relative to the other disk,rollers movable upon rotation of the drive shaft into pressure contactand in rolling engagement with the opposed faces of the disks, gearingconnecting the rollers with the driven shaft for rotation thereof, andmeans for adjusting the spacing of the disks for thereby controllingpositioning of the rollers radially of the disks and varying the speedof rotation of the driven shaft.

21. In a variable speed transmission, the combination of coaxial drivingand driven shafts, a pair of opposed disks disposed coaxially of theshafts and in axially spaced relation thereof, one of the disks beingrotary and the other disk being non-rotary, means interconnecting thedisks for movement thereof to vary the axial spacing therebetween a setof planet rollers in rolling engagement with and between the pair ofdisks, means for mounting the rollers for movement radially of the disksto vary the planetary action of the rollers, planetary gearingconnecting the shafts the planetary gearing including a pinion revolvingwith the driving shaft, and means for rendering the planetary gearingresponsive to variations in the planetary action of the rollers, wherebythe speed ratio between the shafts is varied by movement of the Vrollers radially'of the disks.

22. In a power transmission, a drive shaft, a driven shaft coaxial withthe drive shaft, a pair of disks coaxial with the shafts, the disksbeing axially spaced and having opposed faces converging outwardly fromthe'shafts, rollers mounted on and movable upon rotation of the .driveshaft into pressure contact and in rolling engagement with the opposedfaces of the disks, gearing connecting the rollers with the driven shaftfor rotation thereof, means for holding one disk against rotationrelative to the rollers, means for connecting the other disk forrelative movement of the disks and relative movementof the said otherdisk relative to the rollers,

' and means for adjusting the spacing of the disks for therebycontrolling positioning of the rollers radially of the disks and varyingthe speed of rotation of the driven shaft.

23. In a variable speed transmission, the combination of coaxial drivingand driven shafts, a pair of opposed disks disposed axially of theshafts, a set of planet rollers rotated by the driving shaft in pressurecontact with and between the disks, means interconnecting the disks todetermine the axial spacing therebetween, the disks andtheinterconnecting means therefor being axially movable as a unit toequalize the pressures between the disks and the rollers, the rollersbeing adjustable radially of the disks to vary 'the rate of relativemotionbetween the disks and the rollers, gearing connecting the rollerswith the driven l 12 shaft for rotation thereof'and means responsive tovaria-. tion in the rate of relative motion between the disks and therollers for varying the speed ration between the shafts. 24; In avariable speed transmission, the combination of driving anddrivenshafts, a pair of opposed. coaxial disks in axially spacedrelationand coaxial with the shafts, means interconnecting the disks formovement thereof to vary the axial spacing therebetween a single set ofplanet rollers each in rolling engagement with and between both of thedisks and movable radially thereof to vary the rate of relative motionbetween the rollers and the disks, planetary gearing connecting theshafts, the planetary gearing including a pinion revolving with thedriving shaft, and means for rendering the gearing responsive tovariation in relative motion between the rollers and the disks, wherebythe speed ratio between the shafts is varied by adjustment of therollers.

25. In a power transmission for, changing a variable speed to a constantspeed and vice versa, a variable speed shaft, rollers subjected tocentrifugal force by rotation of the variable speed shaft, a constantspeed shaft, gearing connecting the rollers and the constant speedshaft, and adjustable means acting on the rollers to vary rate ofrotation thereof, said adjustable means including a disk mounted forroller travel thereagainst and overhanging the rollers radially from theaxis of the variable speed shaft for controlling radial outward motionof the rollers from the axis of the variable speed shaft, and means formoving the disk for varying the distance of the path of rollers travelfrom the axis of the variable speed shaft.

whereby the centrifugal force imposed on the rollers is varied. V

26. In a variable speed and power transmission, a driving shaft, adriven shaft, spoke-like members extending radially from one of theshafts, rollers mounted on and movable axially of the spoke-like membersand subjected to centrifugal force by rotation of the driving shaft,gearing connecting the rollers with the other of the shafts, andadjustable means acting on the rollers to vary rate of rotation thereof,said adjustable means in-- eluding a disk mounted for roller travelthereagainst and overhanging the rollers radially from the axis of thevariable speed shaft for controlling radial outward motion of therollers from the axis of the variable speed shaft, and means for movingthe disk for varying the distance of the path of roller travel from theaxis of the driven shaft whereby the centrifugal force imposed on therollers is varied.

27. In a variable speed power transmission, a driving shaft, a drivenshaft, spoke-like members extending from one of the shafts, rollersmounted on and movable axially of the spokes and subjected tocentrifugal force by rotation of the driving shaft, the rollers having aperipheral edge at an angle to the axis of the rollers, gears connectingthe rollers with the other of the shafts, disks mounted in spacedrelation with the rollers therebetween and movable into frictionalengagement with the rollers, the disks having their outer peripheriescloser together than their inner portions for confining the rollers to aselected path of circular travel thereon, and means for moving the disksfor'varyingthe distance of the path of roller travel from the axis ofthe driving shaft whereby the centrifugal force imposed on the rollersis varied.

28. In a variable speed power transmission, a driving shaft, a drivenshaft, spoke-like members extending from one of the shafts, rollersmounted on and movable axially of the spoke-like members and subjectedto centrifugal force by rotation of the driving shaft, movable disksadjustably and frictionally engaged with the rollers at either sidethereof to define an annular path with outwardly convergent walls,pinion gears rotatably mounted on each of the spoke-like members anddriven by the rollers, a bevel gear engaged by the pinion gears andkeyed to the driven shaft, and means for moving the disks and varyingthe distance of the path of roller travel from 13 the axis of thedriving shaft whereby the centrifugal force imposed on the roller isvaried.

29. In a power transmission for changing a variable speed to a constantspeed and vice versa, a driving shaft, a driven shaft, spoke-likemembers extending radially from one of the shafts, rollers mounted onand movable axially of the spoke-like members, pinion gears severallyand rotatably mounted on the spoke-like members, the pinion'gearsseverally having an externally splined hub extension severally enclosingthe spoke-like members, a gear ring keyed to the driven shaft andengaged by the pinion gears, disks having outwardly convergentfrictional surfaces movable toward and away from each other andfrictionally engaging the rollers, and means for moving the disks forvarying the distance of the rollers from the axis of the driving shaftand thereby varying the centrifugal force acting upon the rollers.

References Cited in the file of this patent UNITED STATES PATENTS725,899 Watt Apr. 21, 1903 888,761 Snyder et al. May 26, 1908 1,736,932Meynier Nov. 26, 1929 1,797,953 Gessner Mar. 24, 1931 2,029,042 TurnerJan. 28, 1936 2,079,681 Chilton May 11, 1937 2,100,630 Chilton Nov. 30,1937 2,209,497 Winger et al July 30, 1940

